Coupling

ABSTRACT

The invention among other things relates to a coupling ( 10, 10   a,    10   b ) for transmitting torques from a drive element ( 11, 11   b ) to a driven element ( 12, 12   a,    12   b ), wherein the coupling comprises a drive-side connector ( 13 ), such as a flange, with a plurality of drive-side fastener ( 15   a,    15   b,    15   c ), which are arranged about a drive-side axis of rotation ( 17 ) which is assigned to the drive-side connector and which comprises a load-side connector ( 14 ), such as a flange, with a plurality of load-side fastener ( 16   a,    16   b,    16   c ), and with connecting elements ( 19, 19   a   , 19   b   , 19   c ), such as links, which on the one hand are arranged on one hand on a drive-side fastener and on the other hand on a load-side fastener by means of a articulation joint ( 20 ). The particularity among other things consists in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that the articulation joint is provided by multiple series-connected joints ( 21, 22, 23 ).

The invention initially relates to a coupling according to the preamble of claim 1.

Couplings of this type have been developed and produced by the applicant for some time.

Worth mentioning for example is such a coupling as disclosed in DE 42 05 666 C2. This is a link coupling in which levers that are fastened in an articulated manner between a drive element and a load or driven element can compensate for an angular and axial offset of the inter-connected units up to a certain degree. The links are mounted in rubber bushes, which perform a damping function to a certain degree. The arrangement of rubber elements in the coupling described in the last described publication is required in order to make possible an angular position of drive element and driven element relative to one another. The rubber bushes compensate for the change in spacing between the fastener of a link during a revolution of the coupling.

A further generic coupling is described in the subsequently published EP 2 557 327 A1 going back to the applicant. There, it has already been proposed to arrange the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting elements with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular of 80° to 95°, and preferentially in particular by substantially 90°. This makes possible forming a so-called constant velocity joint, with which higher torques can be transmitted than with a coupling of the prior art.

Starting out from the previously published coupling of the prior art, the invention is based on the object of further developing the known coupling in such a manner that it makes possible the transmission of large torques.

The invention solves this object with the features of claim 1, and is accordingly characterized in particular in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that the articulation joint is provided by multiple joints which are connected in series.

The coupling according to the invention serves for transmitting torques from a drive element to a driven element. The drive element can for example be formed by the flywheel of a motor and the driven element by a shaft.

To connect the coupling with the drive element, the coupling has a drive-side connector. This can for example be a flange, in particular a ring body or the like. On the connector on the drive element side, i.e. the connector which is connected to the drive element in a fixed manner a plurality of drive-side fastener is arranged. These are arranged about a drive-side axis of rotation. The drive-side axis of rotation describes the geometrical axis about which the drive-side connector is rotatable.

For connecting the coupling to the driven element, the coupling comprises a load-side connector. This, too, can be formed for example by a flange or another body. The load-side connector is connected to the driven element, i.e. for example to the driven shaft. The load-side connector likewise comprises a plurality of load-side fastener.

The coupling according to the invention moreover comprises a plurality of connecting elements. These can be for example links or coupling rods. Each connecting element is connected on the one hand to a drive-side fastener and on the other hand to a load-side fastener, each by means of a articulation joint.

To the extent that links are mentioned within the scope of this patent application in the following, this term describes connecting elements quite in general.

The drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged circumferentially spaced from one another. The circumferential spacing with respect to the drive-side axis of rotation amounts to approximately 80° to 100°, advantageously between 85° and 95°, and in particular approximately or substantially 90°.

Through this particular circumferential offset or circumferential spacing a design can be achieved in which the spacing of the fastening elements of drive element and driven element does not change during a revolution of the coupling. Because of this, a constant velocity joint is formed, which manages without intermediate connection of length-compensating elastomer elements.

A substantial feature of the invention consists in that the articulation joint is provided by multiple joints connected in series.

The articulation joint, with which the connecting element is coupled to the drive-side fastener, and equally the articulation joint, with which the connecting element is coupled to the load-side fastener, is provided by a spherical articulation joint in the subsequently published European patent application of the applicant mentioned at the outset, which makes possible three rotatoric degrees of freedom.

The invention recognized that along the three different axes standing perpendicular on top of one another preferred working angles occur during the operation in the case of a generic coupling. The invention furthermore recognizes that for optimizing the working angles or the working paths a spherical articulation joint previously described in the subsequently published patent application can be replaced through multiple joints which are connected in series, one after the other. Because of this a design optimization of the connecting element and of the articulation joints can take place on the one hand. On the other hand, an optimization of the individual joints the requirements for this application purpose can take place in adapting to desired application cases or application purposes.

It is desired in particular to provide a coupling which ensures a long service life with high rotational speeds.

The articulation joint which according to the invention consists of multiple joints connected in series can be formed of different bearings which are connected in series. This can be a combination of multiple different bearings, wherein this combination can comprise for example at least one pivot bearing, in particular a rolling bearing, that for example also a self-aligning roller bearing or a self-aligning ball bearing or for example also a torsion joint.

Of substantial significance is that the articulation joint of multiple joints connected in series makes possible a displaceability of an end of the link relative to the fastener which is adjacent to the other end of the link, along three rotatoric degrees of freedom.

Here, it can be provided with a particularly advantageous configuration of the invention that at least one joint is provided by a pivot bearing. Pivot bearing in terms of the present patent application describes a bearing which in the literature is also described as a radial bearing, which permits a rotatoric movement substantially only about an axis of rotation, the so-called pivot bearing axis.

In terms of this configuration of the invention, the spherical joint which is previously described in the subsequently published patent application can for example be replaced by three pivot bearings which are connected in series, the respective pivot bearing axes stand perpendicular to one another.

In an advantageous configuration of the invention, the joint of the multiple joints which are connected in series which is next to the load-side fastener and/or the drive-side fastener is formed as a pivot bearing. The pivot bearing axis in this case is formed in particular substantially perpendicularly to the drive-side axis of rotation. This configuration takes into account that the largest working angles or working parts during the operation of the coupling occur about this pivot bearing axis.

According to an advantageous configuration of the invention, the pivot bearing comprises lubricating means through which the lifespan of the joint can be significantly increased.

Possible lubricating means are in particular dry lubricating means. Such a dry lubricating means can also be provided by a particular coating.

According to a further advantageous configuration of the invention, the pivot bearing comprises a bearing shell and a bearing shaft which is rotatable about a pivot bearing axis therein. This configuration offers the possibility of arranging the bearing shell in a fixed manner with respect to the drive-side fastener, or in a fixed manner relative to the load-side fastener.

According to a further advantageous configuration of the invention, the pivot bearing is provided by a rolling bearing. This makes possible a very long lifespan and on the other hand utilizing commercially available bearings.

Further advantageously, the rolling bearing is formed by a needle bearing.

According to a further advantageous configuration of the invention, at least one joint is provided by a self-aligning roller bearing or a self-aligning ball bearing. In addition to a rotary movement about a first axis, such a joint can also additionally permit a tilting movement about a second axis, the so-called tilting axis, which is perpendicular to the axis of rotation. The configuration makes it possible to provide the articulation joint of multiple joints connected in series, while making use of as low as possible a number of bearings.

According to a further advantageous configuration of the invention, the pivot bearing axis is substantially aligned perpendicularly to the drive-side axis of rotation.

This configuration takes into account that about this pivot bearing axis the greatest working angles occur during the operation of the coupling.

According to a further advantageous configuration of the invention, a connecting element each comprises a first pivot bearing with a first bearing shell and a first bearing shaft which is rotatable about a first pivot bearing axis therein and a second pivot bearing with a second bearing shell and a second bearing shaft which is rotatable about a second pivot bearing axis therein, wherein the first bearing shell is arranged fixed relative to the drive-side fastener and wherein the second bearing shell is arranged fixed relative to the load-side fastener. Because of this, a simple design can be achieved with a configuration of the connecting element which with respect to a center plane of the connecting element is substantially symmetrical.

The first pivot bearing axis and the second pivot bearing axis are advantageously aligned parallel to one another. This makes possible a particularly simple design.

According to a further advantageous configuration of the invention, the bearing shaft is connected to a spherical surface portion in a fixed manner. The spherical surface portion can for example be engaged over by an eye portion of the connecting element. The coupling element in this respect can comprise a first joint provided by the pivot bearing described above, in particular rolling bearing and a second joint which is connected in series with the pivot bearing, which is provided by the spherical surface portion and the eye portion.

While the pivot bearing can allow working angles which occur during the operation of the coupling of for example 6° to 15°, in particular 6° to 12°, in particular advantageously between 8° and 11°, the second joint which is formed by the spherical surface portion and eye portion can allow substantially smaller working angles of for example only one or two degrees, wherein the rotary movement that is allowed by the second joint takes place about an axis of rotation which is substantially perpendicular to the pivot bearing axis of the pivot bearing.

According to an advantageous configuration of the invention, a further joint can be provided by a torsion joint. The torsion joint can for example be provided by a connecting element which is altogether configured torsionally soft. To this end, the connecting element based on its longitudinal center axis can comprise a predetermined bending point in its middle region, which is formed for example by a cross-sectional tapering of the connecting element. To this end it can be provided that the first end of the connecting element is designed torsionable about a longitudinal center axis of the connecting element relative to a second end of the connecting element. This makes possible a particularly simple design of a connecting element and the possibility of keeping the number of the joints that have to be provided in a connecting element altogether low.

Instead of a connecting element of the prior art, which is connected on both ends to the drive-side fastener on the one hand and the load-side fastener on the other end via a spherical articulation joint, a connecting element according to the invention can comprise a pivot bearing each on both ends and a second joint, which is provided for example through a spherical surface portion and an eye portion, or which at any rate allows a tilting movement or pivot movement about an axis that is perpendicular to the pivot bearing axis of the first joint, and provides a third joint, for example through a torsionable connecting element, in order to make possible the same numbers of degrees of freedom as a spherical joint.

According to an advantageous configuration of the invention, the drive-side fastener are arranged in a common radial plane of the drive-side axis of rotation. Advantageously, the drive-side fastener are arranged on a common radius about the drive-side axis of rotation.

Further advantageously, the load-side connector has a drive-side axis of rotation. Further advantageously, the load-side fastener are arranged in a common radial plane of the load-side axis of rotation.

Finally, it can be additionally provided advantageously that the load-side fastener are arranged on a common radius about the load-side axis of rotation.

Finally it can be advantageously provided that the radius on which the drive-side fastener are arranged about the drive-side axis of rotation and the radius, on which the load-side fastener are arranged about the load-side axis of rotation, are identical in the amounts.

The number of the connecting elements can be selected as desired. Advantageously, connecting element trios can be provided, so that in each case between a drive-side connector and a load-side connector three connecting elements are provided.

Advantageously, the links which are provided in each case between a drive-side connector and a load-side connector are arranged equidistantly from one another in circumferential direction.

The invention furthermore relates to a coupling which is developed further in such a manner that it makes possible the transmission of large torques.

This coupling is characterized in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged with respect to the drive-side axis of rotation by 80° to 100°, in particular by 85° to 90°, further particularly by substantially 90° circumferentially spaced from one another, and in that the connecting element each is substantially formed dumb-bell-shaped and comprises a cross-sectional tapering or cross-sectional weakening in the middle.

Through the dumb-bell-like design and a cross-sectional weakening which is provided in the middle with respect to a longitudinal center axis of the link, a torsionable configuration of the connecting element is made possible. Because of this, omitting pivot bearing joints, also omitting spherical joints can be achieved without reducing the number of the degrees of freedom.

Through the substantially dumb-bell-like design of the connecting element one succeeds in accommodating multiple, in particular two, joints connected in series, for example a joint comprising a pivot bearing and a spherical portion in the region of the ends of the connecting element.

The invention furthermore relates to a coupling according to the preamble of claim 17.

The invention is again based on the object of further developing the known coupling in such a manner that it makes possible the transmission or large torques.

The invention solves this object with the features of claim 17, in particular with those of the characterizing part, and accordingly is characterized in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged with respect to the drive-side axis of rotation by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90° circumferentially spaced from one another, and in that the connecting element is designed torsionable in such a manner that its first end which is connected to the drive-side fastener in an articulated manner is twistable about a longitudinal center axis of the connecting element on the end which is connected to the load-side fastener in an articulated manner.

The principle of the invention substantially consists in that the connecting element is configured torsionable. The torsionable configuration can be achieved in particular through a torsionally soft design of the connecting element. This makes possible a twisting of its first end relative to its second end. Because of this, the number of the joints on a connecting element can be altogether kept low.

The invention furthermore relates to a coupling according to the preamble of claim 20. The invention is again based on the object of further developing the known coupling in such a manner that it makes possible the transmission of large torques.

The invention solves this object with the features of claim 20, in particular with those of the characterizing part, and is characterized in particular in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element are arranged with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that the articulation joint comprises a pivot bearing which allows a rotary movement only about a pivot bearing axis.

The principle of the invention substantially consists in forming the articulation joint in such a manner that it comprises at least one pivot bearing, which allows a rotary movement only about a pivot bearing axis. Through this special, optimized design configuration of the bearing it can be achieved that a rolling bearing is provided. This can make possible a long service life of a coupling even when large torques with high rotational speed are transmitted.

According to a further advantageous configuration of the invention, two couplings of the type described above are connected to one another with the help of a shaft. This makes it possible to provide a coupling which also allows a radial offset between drive element and driven element or can compensate for such. Such a double-cardanic design is known per se from the prior art, however not with the provision of the particular geometry of the drive-side and load-side fastener and of the connecting elements.

With respect to the couplings described above, also if these originate from different or independent claims, it is true that the different couplings can also have individual or multiple features of the respective other couplings described. For the following FIG. description of the illustrated embodiments it is also true that features, even to the extent that these are only described with one illustrated embodiment can also be provided with other illustrated embodiments.

Further advantages of the invention are obtained with the help of the subclaims which have not been quoted and from the following description of the illustrated embodiments shown in the figures. Therein it shows:

FIG. 1 an illustrated embodiment of a coupling according to the invention in double-cardanic configuration in a perspective, schematic view,

FIG. 1 a the illustrated embodiment of FIG. 1 according to the view arrow Ia in FIG. 1 in a further schematic view,

FIG. 2 highly schematically, the coupling of FIG. 1 a according to view arrow II-II in FIG. 1 a, wherein the shaft and the in FIG. 1 a left coupling have been omitted,

FIG. 3 the illustrated embodiment of the coupling of FIG. 2 in a simplified, schematic view approximately according to the view arrow III in FIG. 2 in individual representation,

FIG. 4 a connecting element of a coupling according to the invention, represented highly schematically, in a schematic individual view,

FIG. 5 the connecting element of FIG. 4 approximately according to the view arrow V in FIG. 4 in a bottom view,

FIG. 6 a partly sectioned, schematic view through the connecting element of FIG. 5, approximately along the section line VI-VI,

FIG. 7 a partly sectioned, schematic view through the connecting element of FIG. 5, approximately along the section line VII-VII,

FIG. 8 a partly sectioned, schematic view through the connecting element approximately along the section line VIII-VIII in FIG. 6,

FIG. 9 a partly sectioned, schematic view through the connecting element, approximately along the section line IX-IX in FIG. 5,

FIG. 10 a schematic diagram intended to show the series connection of joints according to the invention for the different bearings in a three dimensional view making use of schematic connection symbols, and

FIG. 11 in a representation which is comparable to the representation of FIG. 10 a diagram sketch of a further schematic illustrated embodiment.

The coupling which in its entirety is designated 10 in the drawings is described in the following by means of the illustrated embodiments in the drawings. At the outset of the following description it is mentioned that for the sake of clarity same parts or parts or elements which are comparable to one another, also to the extent to which these can be assigned to different illustrated embodiments, are marked with same reference characters, partly with the addition of lower-case characters.

The coupling of FIG. 1 is altogether marked with 10 and comprises a first coupling 10 a and a second coupling 10 b, between which a shaft 39 is arranged. The coupling 10 is shown further schematically in a partly sectioned schematic view compared with the representation of FIG. 1 in FIG. 1 a.

The coupling 10 a of FIG. 1 a serves for connecting a merely schematically shown drive element 11 to a driven element 12 a. The driven element 12 a in the illustrated embodiment of FIG. 1 a is provided by the shaft 39, and at the same time constitutes the drive element 11 b for the coupling 10 b. The coupling 10 b serves to connect the drive element 11 b to the merely schematically shown driven element 12 b.

The shaft 39 in the terminology of the present patent application the driven element 12 a of the first coupling 10 a and simultaneously the drive element 11 b of the second coupling 10 b.

While the illustrated embodiment of FIGS. 1 and 1 a shows a double-cardanic arrangement of two couplings 10, 10 a, only one coupling 10 each is provided with other illustrated embodiments of the invention. Such an embodiment is described initially by means of the FIGS. 2 and 3, namely by means of the right coupling 10 a of FIG. 1 a.

A coupling 10 a comprises a drive-side connector 13, which is connected to the drive element 11 in a fixed manner. This can be for example a ring-shaped flange 14 which is evident for example in FIG. 2. FIG. 2 however shows—corresponding to the view of the view arrow II-II in FIG. 1 a—the load-side flange 14. The drive-side ring-shaped flange 13 which is assigned to this coupling 10 a however is designed identically to the load-side flange 14, which provides the load-side connector.

On the flange 13, drive-side fastener 15 a, 15 b, 15 c are arranged. The drive-side fastener 15 are connected to the drive-side connector 13 in a fixed manner. The drive-side fastener 15 can for example be provided by holding elements, on which the bearing shells 25 of articulation joints to be described later on are connected in a fixed manner.

The drive-side connector 13 is connected to the drive element 11 in a fixed manner. The drive element 11 can for example be provided by the flywheel of a motor.

The coupling 10 a additionally comprises a load-side connector 14. This in turn is connected to the driven element 12 a in a fixed manner. The load-side connector 14 comprises load-side fastener 16 a, 16 b, 16 c, each of which are connected to the load-side connector 14 in a fixed manner.

FIG. 1 a makes it clear that a drive-side fastening point (for example the drive-side fastening point 15 a) each is connected to a load-side fastener (according to FIG. 1 a to the fastening point 16 b) each through a connecting element 19 a.

In the illustrated embodiment of the Figures, each coupling 10 a comprises three connecting elements 19 a, 19 b, 19 c each, which can also be described as links.

The with respect to FIG. 1 a left coupling 10 b also comprises three links 19 d, 19 e, 19 f.

FIGS. 1 a, 2 and 3 show the links 19 a, 19 b, 19 c each only highly schematically. The FIGS. 4 to 9 each show a link 19 in a representation which by contrast is detailed.

The drive-side connector 13 is assigned a drive-side axis of rotation 17 and the load-side connector 14 is assigned a load-side axis of rotation 18.

In the illustrated embodiments of FIGS. 1 a and 2, the drive-side axis of rotation 17 and the load-side axis of rotation 18 are arranged aligned with one another. The coupling 10 a however serves exactly in order to compensate for axial offset, radial offset or angular offset. The drive-side axis of rotation 17 and the load-side axis of rotation 18 can therefore also be positioned at an angle or also parallel to one another.

In a double-cardanic arrangement of two couplings 10 a and 10 b according to 1 and 1 a, the drive-side axis of rotation 17 of the first coupling 10 a and the load-side axis of rotation 18 b of the second coupling 10 b can be subject to a correspondingly enlarged axial offset or angular offset, or also compensate for a radial offset.

FIG. 2 makes it clear that the load-side fastener 16 a, 16 b, 16 c are arranged at a same radius 36 a, 36 b, 36 c based on the load-side axis of rotation 18.

The drive-side fastener 15 a, 15 b, 15 c which are not shown in FIG. 2 are also arranged at the same radius 36 d, 36 e, 36 f based on the drive-side axis of rotation 17.

FIG. 2 merely shows the load-side fastener 16 a, 16 b, 16 c of the coupling 10 a and merely indicates the positions of the drive-side fastener 15 a, 15 b, 15 c.

All drive-side fastener 15 a, 15 b, 15 c and all load-side fastener 16 a, 16 b, 16 c are each arranged in a common radial plane 35 a, 35 b.

FIG. 2 makes it clear that a load-side fastener (e.g. 16 a) each is spaced from one another at a circumferential angle w relative to the drive-side fastener (15 b) of a connecting element (19 b), which in the illustrated embodiment amounts to exactly 90°.

The remaining drive-side fastener located opposite one another and the load-side fastener of the other connecting element 19 a, 19 c are each—insofar as each belong to a connecting element—circumferentially spaced from one another by 90° each.

Through this particular circumferential spacing one succeeds in forming a constant velocity joint with the described advantageous characteristics.

By means of the FIGS. 4 to 9, a concrete, particularly advantageous configuration of a connecting element 19, the so-called link, is now discussed in more detail.

Even the perspective view of FIG. 4 shows that the link 19 is substantially formed dumb-bell-like or bone-like, with a first substantially spherically formed end 33 and a second substantially spherically formed end 34. In addition, the link 19 comprises a middle portion 40, which with respect to the two spherical ends 33, 34 is configured narrow so that a dumb-bell or bone shape is obtained. The middle portion 40 in addition has a cross-sectional tapering 37 or cross-sectional weakening, which will still be discussed in more detail later on.

Making use of FIG. 1 a, in particular of the coupling 10 a shown there, it is indicated exemplarily that the connecting element 19 b is connected to the drive-side fastener 15 b via a first articulation joint 20 a and to the load-side fastener 16 a via a second articulation joint 20 b.

The articulation joints 20 a, 20 b each consist of three joints 21, 22 and 23 connected in series as will be explained now in the following by means of the FIGS. 4 to 9.

The first joint 21 in the illustrated embodiment is formed as a pivot bearing 24, and is initially illustrated by means of the FIGS. 6 and 7: the pivot bearing 24 comprises a bearing shell 25, which is arranged fixed relative to the drive-side fastener. Based on the link 19 b of FIG. 1 a, the bearing shell 25 of the articulation joint 20 a of this link 19 b is thus arranged fixed relative to the drive-side-fastener 15 b, which is not shown in the FIGS. 6 and 7.

Within the bearing shell 25, a bearing shaft 26 which is rotatable about the pivot bearing axis 27 is arranged. The bearing shaft 26 is a substantially cylindrical body which comprises a bulging region 41.

In the bulging region 41, the bearing shaft 26 is widened and projects out of the bearing shell 25 transversely to the pivot bearing axis 27.

The pivot bearing 24 allows a rotary movement of the bearing shaft 26 only about the pivot bearing axis 27, but not about a further axis.

The pivot bearing 24 is formed as a so-called rolling bearing. This means that between the outside 42 of the bearing shaft 26 and the inside 43 of the bearing shell 25 multiple rolling elements, in particular balls, or in a preferred illustrated embodiment, cylindrical rollers are arranged. Making use of cylindrical rollers, these are also called needles, the rolling bearing 28 thus formed is embodied as a so-called needle bearing in the advantageous illustrated embodiment.

A rotation of the bearing shaft 26 about the axis of rotation 27 is effected in this regard subject to the rotation of multiple cylindrical rollers which are not shown in the illustrated embodiment of FIG. 7.

The second joint 22 is formed by a spherical surface portion 30, which is arranged on the bulging region 41. The spherical surface portion 30 is engaged over by an eye portion 31, which is again arranged fixed relative to the middle portion 40 of the link.

The spherical surface portion 30 allows a spherical movement within certain, small angular ranges. Above all, the second joint 22 formed through the spherical surface portion 30 and the eye portion 31 allows a rotary movement of the middle portion 40 of the connecting element 19 relative to the bearing shaft 26 about an axis of rotation which is marked with 44 in the FIGS. 6 and 8. The axis of rotation 44 stands perpendicularly with respect to the pivot bearing axis 27.

Finally, the articulation joint 20 additionally comprises a third joint 23, which is provided by a bending joint or torsion joint 32.

Providing a torsion joint is favored by a cross-sectional tapering 37 of the link.

FIG. 6 shows that in the region of the ends 33, 34 the link 19 has a width GB, which is substantially greater than the width KB in the middle of the link 19 based on its longitudinal center axis 38.

Through the weakening of the cross-section of the link 19 exactly in the region of its middle (at 37), the link element 19 is altogether configured torsionally soft and torsionable about its longitudinal center axis 38. In the illustrated embodiment of a connecting element shown in FIG. 9, its torsionally soft configuration is specifically provided through the use of two substantially rectangular profiles which are open toward the outside.

While in the case of further illustrated embodiments which are not shown the described cross-sectional weakening in the middle region of the connecting element need not be mandatorily present, the torsionable configuration in the illustrated embodiment is at least favored through the arrangement of the middle cross-sectional tapering. The one end 34 of the link 19 in this respect is torsionable, i.e. relatively twistable, based on the longitudinal center axis 38, relative to the second end 34 of the link within a predetermined angular range during the operation of the coupling 10.

The articulation joint 20 in the illustrated embodiment is provided by a first articulation joint 24 formed as a radial bearing, a second joint 22 formed as a spherical joint and by a third joint 23 formed as a torsion joint, wherein these three joints are connected in series.

The three rotary axes 27, 44, 38, which are provided by the three different joints 21, 22, 23, all stand on one another perpendicularly. The three rotary axes or joint axes 27, 44, 38 all intersect one another in one point, the so-called point of articulation.

It is clear to the person skilled in the art that other designs and series connections of such joints are included in the invention.

With respect to the design of the second joint 22, as is shown in particular in the FIGS. 7 and 8, it is mentioned that because of this a tilting of the connecting element about the tilting axis or axis of rotation 44 is primarily achieved. A rotary movement about the axis of rotation 27 of the first joint 21 which is possible in principle in the case of such joints 22, which make use of spherical surface portions 30, will not take place during the operation as a rule since the friction between the portions 30 and 31 is substantially higher than the friction which is accompanied by a rotary movement about the rolling bearing 21 about the axis of rotation 27.

The invention recognizes that with generic couplings 10 a typical working angle during the operation of the coupling about the pivot bearing axis 27 can be relatively large. Thus, the working angle α shown for example in FIG. 6 between the bearing shell 25 in dashed and in continuous lines is approximately 5° to 9°, in particular approximately 6° in size and is to illustrate that larger working angles are to be expected here.

For this reason, which is evident in particular also in FIG. 6, the two pivot bearing axes 27, 27 d on the two articulation joints 20 a, 20 b on a link 19 are orientated parallel to one another.

In addition, it is appropriate to form these pivot bearings 24, 24 d as rolling bearings.

Compared with this, only a very small angle β, the so-called tilting angle, of for example 0.05° to 2°, in particular an angle between 1° and 2°, or—depending on the illustrated embodiment, an angle of approximately between 0.1° and 0.4° is to be expected as a working angle about the axis of rotation 44 during the operation of the coupling.

Finally, based on the longitudinal center axis 38 of the link 19, only a minor portion, with a working angle of approximately 1° to 2° is to be expected. Depending on embodiment, it can also be provided however that the largest working angles, of for example between 6° and 15°, will be employed here.

The exact angles are obviously dependent on the selected dimensions, e.g. on the length of the links, on the installation length of the coupling, on the radial angular offsets and axial offsets to be compensated for and on the magnitude of the torques to be transmitted as well as ultimately the rotation speed as well.

Finally, there is the additional possibility in particular to replace the joint 22 which is formed by the spherical surface portion 30 and eye portion 31 by a further pivot bearing, which permits rotation only about a single axis of rotation 44.

Finally, the torsion joint 32 can also be replaced with such a articulation joint.

The configuration of the invention shown in the drawings is suitable in particular for fast-rotating couplings, i.e. for couplings 10 which operate with high rotational speeds and transmit high torques.

The spherical articulation joint which is described in the subsequently published patent application of the prior art, which makes possible three rotatoric degrees of freedom, is functionally split according to the invention over three joints, each of which individually allow one rotatoric degree of freedom.

The series-connection of joints in the described manner according to the invention equally makes it possible that an end of the link relative to the drive-side or load-side fastening point fixed on the other end of this link can assume any point in space within predetermined limits, subject to utilizing the three rotatoric degrees of freedom.

Finally it is pointed out here that instead of the described articulation joints and torsion joints, axial bearings, i.e. sliding joints, can also be employed. Under certain conditions, elastomer elements can also be employed as bearing components.

In contrast with the previously described spherical joint and for providing the multiple rotatoric degrees of freedom, at least one series connection of two different bearings is provided according to the invention.

Insofar as the terms self-aligning ball bearing or self-aligning roller bearing are used in this patent application, reference can be made to their definition that is usual in the prior art. It relates to bearings which in addition to a rotation about the center axis also make possible a pivoting or tilting out of a center position about a few angular degrees about an axis that is perpendicular to the center axis.

Based on the highly schematic representation of FIG. 10, it is now explained that the first joint 21 a of a articulation joint 20, and the second joint 22 a of the articulation joint 20 and the third joint 23 a of the articulation joint 20 can be formed by bearings which are configured in any design.

Thus, FIG. 10, in a highly schematic, block diagram-like representation, shows that the articulation joint 20 can comprise a first joint 21 a, which can be formed of a bearing shell 25 a, 25 b which on an end side (i.e. on the fastener side) can be held in a fixed manner. In the bearing shell 25 a, 25 b formed thus, a bearing shaft 26 a which is rotatable about a geometrical axis of rotation 27 a is mounted.

The bearing shaft 26 a is movement-uniformly connected to a further bearing shaft 26 c. The latter in turn is rotatably mounted in a further bearing shell, formed through the bearing shell parts 25 c, 25 d, about the geometrical axis of rotation 44 a relative to the bearing shell 25 c, 25 d.

The bearing shell parts 25 c, 25 d in turn are connected to a bearing shell 25 e in a rotationally fixed manner. The bearing shell 25 e provides a pivot bearing for a further bearing shaft 26 e. The latter is rotatable about a geometrical axis 38 b relative to the bearing shell 25 e.

The geometrical axes of rotation 27 a, 44 a and 38 b all stand perpendicularly to one another and all intersect one another in the point of articulation G.

How the individual bearings are concretely designed is dependent on the individual illustrated embodiment. Decisive is that this series connection of joints or bearings 21 a, 22 a, 23 a makes possible three rotatoric degrees of freedom of the bearing shaft 26 e relative to the fastening point 46. The fastening point 46 in this case corresponds to the drive-side or load-side fastener 15, 16. The bearing shaft 26 e in this consideration corresponds to the other end region of the corresponding connecting element or link which is arranged distally to the above-described fastening point 15, 16 on the drive element side or the driven element side.

FIG. 11 shows an illustrated embodiment of a articulation joint 20 in a further schematic diagram, in which a first joint 21 b is provided by a bearing shell 25 f, in which a bearing shaft 26 f is rotatably arranged about a geometrical axis 27 b. The bearing shaft 26 f is connected in a fixed manner to bearing shell parts 25 g and 25 h of a second joint 22 b. In the bearing provided by the bearing shells 25 g, 25 h or relative to the bearing, a bearing shaft 26 g is rotatable about the geometrical axis 44 b.

The bearing shaft 26 g in turn is connected to a bearing shaft 26 i in a fixed manner. The bearing shaft 26 i is rotatable about a geometrical axis 38 b relative to a bearing which is provided of bearing shell parts 25 i and 25 j. Again, the three geometrical axes of rotation 27 b, 44 b and 38 b intersect in a point of articulation G.

In this illustrated embodiment, too, a articulation joint 20 is provided which makes possible the three rotatoric degrees of freedom. Again, the concrete design configuration of the individual bearings for providing a articulation joint 20 according to the invention is not relevant. 

1. A coupling (10, 10 a, 10 b) for transmitting torque from a drive element (11, 11 b) to a driven element (12, 12 a, 12 b), the coupling comprising a drive-side connector (13), such as a flange, with a plurality of drive-side fasteners (15 a, 15 b, 15 c) angularly spaced around a drive-side axis (17) of the drive-side connector, and a load-side connector (14), such as a flange, with a plurality of load-side fasteners (16 a, 16 b, 16 c) and connecting elements (19, 19 a, 19 b, 19 c), such as links, each connected at one end to a respective one of the drive-side fasteners and connected via a swivel (2) at the other end to a respective one of the load-side fasteners, characterized in that each drive-side fastener and the respective load-side fastener coupled to it by the respective connecting element are angularly offset relative to the drive-side axis by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that each swivel joint is formed by a plurality of series-connected joints (21, 22, 23).
 2. The coupling according to claim 1, characterized in that at least one joint (21) is provided by a pivot bearing (24).
 3. The coupling according to claim 2, characterized in that the pivot bearing comprises a bearing shell (25) and a bearing shaft (26) which is rotatable about a pivot bearing axis (27) therein.
 4. The coupling according to claim 3, characterized in that the bearing shell (25) is arranged fixed relative to the drive-side fastener (15) or fixed relative to the load-side fastener (16).
 5. The coupling according to claim 2, characterized in that the pivot bearing is provided by a rolling bearing, in particular by a needle bearing.
 6. The coupling according to claim 1, characterized in that at least one joint comprises a self-aligning roller bearing or a self-aligning ball bearing.
 7. The coupling according to claim 2, characterized in that a pivot bearing axis (27) of the pivot bearing is substantially aligned perpendicularly to the drive-side axis of rotation (17).
 8. The coupling according to claim 1, characterized in that a connecting element (19) each comprises a first pivot bearing (24) with a first bearing shell and a first bearing shaft which is rotatable about a first pivot bearing axis (27) therein and a second pivot bearing (24 d) with a second bearing shell and a second bearing shaft which is rotatable about a second pivot bearing axis (27 d) therein, wherein the first bearing shell is arranged fixed relative to the drive-side fastener and wherein the second bearing shell is arranged fixed relative to the load-side fastener.
 9. The coupling according to claim 18, characterized in that the first pivot bearing axis (27) and the second pivot bearing axis (27 d) are aligned parallel to one another.
 10. The coupling according to claim 3, characterized in that the bearing shaft (26) is connected to a spherical surface portion (30) in a fixed manner.
 11. The coupling according to claim 10, characterized in that the spherical surface portion is engaged over by an eye portion (31) of the connecting element (19).
 12. The coupling according to claim 1, characterized in that at least one joint (23) is provided by a torsion joint (32).
 13. The coupling according to claim 1, characterized in that a first end (33) of the connecting element (19) is torsionable about a longitudinal center axis (38) of the connecting element relative to a second end (34) of the connecting element.
 14. The coupling according to claim 1, characterized in that the drive-side fastener (15 a, 15 b, 15 c) are arranged in a common radial plane (35 a) of the drive-side axis of rotation (17).
 15. The coupling according to claim 1, characterized in that the drive-side fastener are arranged on a common radius (36 a, 36 b, 36 c, 36 d) about the drive-side axis of rotation.
 16. The coupling according to claim 1, characterized in that the load-side connector (14) comprises a load-side axis of rotation (18).
 17. The coupling according to claim 16, characterized in that the load-side fastener (16 a, 16 b, 16 c) are arranged in a common radial plane (35 b) of the load-side axis of rotation.
 18. The coupling according to claim 16, characterized in that the load-side fastener (16) are arranged on a common radius about the load-side axis of rotation (18), wherein in particular the radius, on which the drive-side fastener are arranged about the drive-side axis of rotation (17), and the radius, on which the load-side fastener are arranged about the load-side axis of rotation (18) are identical in the amount.
 19. A coupling (10, 10 a, 10 b) for transmitting torques from a drive element (11) to a driven element (12), wherein the coupling comprises a drive-side connector (13), such as a flange, with a plurality of drive-side fastener (15 a, 15 b, 15 c), which are arranged about a drive-side axis of rotation (17) which is assigned to the drive-side connector, and which comprises a load-side connector (14), such as a flange, with a plurality of load-side fastener (16 a, 16 b, 16 c) and with connecting elements (19, 19 a, 19 b, 19 c), such as links, which on the one hand are arranged on a drive-side fastener and on the other hand on a load-side fastener by means of a articulation joint (20), characterized in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element is arranged with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that the connecting element (19) is designed torsionable in such a manner that its first end (33) which is connected at the drive-side fastening point in an articulated manner is rotatable about a longitudinal center axis (38) of the connecting element on the end (34) which is connected to the load-side fastening point in an is articulated manner.
 20. A coupling (10, 10 a, 10 b) for transmitting torques from a drive element (11) to a driven element (12), wherein the coupling comprises a drive-side connector (13), such as a flange, with a plurality of drive-side fastener (15 a, 15 b, 15 c), which are arranged about a drive-side axis of rotation (17) assigned to the drive-side connector, and which comprises a load-side connector (14), such as a flange, with a plurality of load-side fastener (16 a, 16 b, 16 c), and with connecting elements (19, 19 a, 19 b, 19 c), such as links, which on the one hand are arranged on a drive-side fastener and on the other hand on a load-side fastener by means of a articulation joint (20), characterized in that the drive-side fastener and the load-side fastener which is coupled to the former by means of a connecting element is arranged with respect to the drive-side axis of rotation circumferentially spaced from one another by 80° to 100°, in particular by 85° to 95°, further particularly by substantially 90°, and in that the articulation joint (20) comprises a pivot bearing (24) allowing a rotary movement only about one pivot bearing axis (27) and/or a self-aligning roller bearing and/or a self-aligning ball bearing. 